EP2210708B1 - Outil d'impact rotatif - Google Patents

Outil d'impact rotatif Download PDF

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Publication number
EP2210708B1
EP2210708B1 EP10000820A EP10000820A EP2210708B1 EP 2210708 B1 EP2210708 B1 EP 2210708B1 EP 10000820 A EP10000820 A EP 10000820A EP 10000820 A EP10000820 A EP 10000820A EP 2210708 B1 EP2210708 B1 EP 2210708B1
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EP
European Patent Office
Prior art keywords
mode
speed
reduction
unit
planetary
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP10000820A
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German (de)
English (en)
Other versions
EP2210708A3 (fr
EP2210708B8 (fr
EP2210708A2 (fr
Inventor
Fumiaki Sekino
Kenichiro Inagaki
Yutaka Yamada
Hiroyuki Tsubakimoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Panasonic Electric Works Power Tools Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
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Publication of EP2210708A2 publication Critical patent/EP2210708A2/fr
Publication of EP2210708A3 publication Critical patent/EP2210708A3/fr
Publication of EP2210708B1 publication Critical patent/EP2210708B1/fr
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Publication of EP2210708B8 publication Critical patent/EP2210708B8/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B45/00—Hand-held or like portable drilling machines, e.g. drill guns; Equipment therefor
    • B23B45/008—Gear boxes, clutches, bearings, feeding mechanisms or like equipment
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B25B21/026—Impact clutches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/141—Mechanical overload release couplings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three engaging means

Definitions

  • the present invention relates to a rotary impact tool and, more specifically, to a rotary impact tool capable of changing over an impact mode and a drill driver mode.
  • a multi-purpose rotary impact tool capable of changing over an impact mode in which bolts, nuts or screws are tightened by an impact mechanism having a hammer and an anvil and a drill driver mode in which drilling tasks such as pilot hole forming and screw tightening are performed while restraining the impact operation of the impact mechanism.
  • Patent Document 1 discloses a rotary impact tool that can be changed over between a low speed mode in which a planetary reduction mechanism operates and a high speed mode in which the planetary reduction mechanism does not operate.
  • the high speed mode is used as an impact mode and the low speed mode as a drill driver mode.
  • Patent Document 2 discloses a rotary impact tool in which a high speed mode can be changed between an impact mode and a drill driver mode depending on whether an impact mechanism is restrained or released.
  • the drill driver mode can be changed between two different speed modes, i.e., a low speed mode for drilling purposes and a high speed mode for screw-tightening purposes.
  • the drill driver mode of the rotary impact tool disclosed in Patent Document 1 lies generally halfway between a high speed mode and a low speed mode available in a drill-driver-single-function rotary tool, such as an electric drill or the like.
  • the rotary impact tool disclosed in Patent Document 1 poses a problem in that the screw tightening speed thereof is slower than that available in the high speed mode of the single-function rotary tool.
  • Another problem resides in that the rotary impact tool cannot perform an operation of drilling large-diameter holes as is available in the low speed mode of the single-function rotary tool.
  • the present invention provides a rotary impact tool operable both in an impact mode having at least one speed and in a drill driver mode having two or more speeds and a reduction ratio different than that of the impact mode, the performance of the rotary impact tool in the drill driver mode being substantially equivalent to the performance available in high speed and low speed modes of a drill-driver-single-function rotary tool, the rotary impact tool being designed to minimize the increase in the size of a speed changer mechanism to thereby improve the ease of use of the rotary impact tool in the drill driver mode.
  • a rotary impact tool including: a drive power source for producing rotational power; a drive shaft driven by the rotational power supplied from the drive power source; an output shaft operatively connected to the drive shaft for receiving the rotational power; an impact mechanism operatively couplable with the drive shaft, the impact mechanism including a hammer and an anvil; a changeover unit for changing over an impact mode in which the impact mechanism is operated and a drill driver mode in which the rotational power produced by the drive power source is transferred to the output shaft without operating the impact mechanism; and a multi-stage speed reduction mechanism for transferring the rotational power produced by the drive power source to the output shaft through the drive shaft at variable speeds in at least three speed modes including a low speed mode, a middle speed mode and a high speed mode, wherein the multi-stage speed reduction mechanism includes at least two planetary speed changer units shiftable between a reduction state and a non-reduction state and at least one speed reducer unit operable in a reduction state at all times,
  • the respective modes can be set to have the reduction ratios resulting from the reduction operation performed in two or more stages. Furthermore, two or more speeds become available in the drill driver mode with the reduction ratios differing from that of the impact mode.
  • the drill driver mode of the present rotary impact tool is substantially the same as the drill driver mode of the conventional drill-driver-single-function rotary tool for use in tightening screws and drilling large-diameter holes. This helps enhance the ease of use of the present rotary impact tool. Since two-stage speed reduction is performed by the speed reducer unit and the speed changer units in the impact mode, it is possible to achieve greater speed reduction than the conventional impact mode in which speed reduction is performed in a single stage and the reduction ratio is from about 1/7 to 1/8.
  • the outer diameter of the multi-stage speed reduction mechanism can be made smaller than that of the conventional mechanism in which the reduction ratio comparable to that of the present invention is achieved by single-stage reduction. This helps minimize the increase in size.
  • one of the two planetary speed changer units may come into the reduction state in the middle speed mode and the other may come into the reduction state in the high speed mode, the speed ratio between the high speed mode and the middle speed mode being set equal to the ratio between the reduction ratios of the two planetary speed changer units.
  • the speed changer unit coming into the reduction state in the high speed mode differs from the speed changer unit coming into the reduction state in the middle speed mode.
  • the speed ratio between the high speed mode and the middle speed mode is equal to the ratio between the reduction ratios of the speed changer units used in the respective modes. This makes it possible to easily set the reduction ratios in the respective modes. Accordingly, it is possible to set the drill driver mode with a reduction ratio closer to that of the conventional drill-driver-single-function rotary tool. This improves the ease of use of the rotary impact tool in the drill driver mode.
  • the planetary speed changer unit coming into the reduction state in the middle speed mode may includes a IV-type planetary gear unit having a sun gear, a ring gear and a stepped planetary gear, the stepped planetary gear including a large-diameter gear portion and a small-diameter gear portion, the large-diameter gear portion differing in teeth number and outer diameter from the small-diameter gear portion, the large-diameter gear portion engaging with the sun gear, the small-diameter gear portion engaging with the ring gear.
  • the speed changer unit coming into the reduction state in the middle speed mode which needs to have greater speed reduction than the speed changer unit coming into the reduction state in the high speed mode, is formed of a IV-type planetary gear unit. Therefore, the planetary gear of the speed changer unit coming into the reduction state in the middle speed mode is formed of a stepped planetary gear. This makes it possible to realize an increased speed reduction without having to reduce the size of the sun gear or to increase the outer diameter of the ring gear. Accordingly, it is possible to prevent the increase in the outer diameter of the speed changer units which would otherwise be required to secure the strength of the sun gear. This assists in minimizing the increase in the size of the rotary impact tool.
  • the speed reducer unit may be a first planetary reduction unit arranged near the drive power source in the multi-stage speed reduction mechanism.
  • the speed reducer unit performing no speed changing operation is used as a first planetary reduction unit that directly receives torque from a motor and rotates at an increased speed. Therefore, the respective gears of the first planetary reduction unit are not shifted when changing over the modes. This makes it possible to prevent occurrence of gear damage or other problems during the mode changing operation, thereby improving the ease of use of the rotary impact tool.
  • the changeover unit may include engagement portions respectively provided in the anvil and the drive shaft engaging with the hammer and a connector member arranged to engage with the engagement portions, and wherein the drill driver mode and the impact mode are changed over by changing over a state in which the connector member engages with the engagement portions to interconnect the anvil and the drive shaft against relative rotation and a state in which the connector member does not engage with at least one of the engagement portions.
  • the impact mode can be easily converted to the drill driver mode by bringing the connector member into engagement with the engagement portions to interconnect the anvil and the drive shaft against relative rotation. Since the torque is transferred to the output shaft without passing through the hammer, it is possible to deactivate the impact mechanism in the drill driver mode.
  • This helps simplify the configuration of the changeover unit used in changing over the impact mode and the drill driver mode. Accordingly, it is possible to prevent the increase in the size of the rotary impact tool, which would otherwise occur when the changeover unit becomes complex. It is also possible to easily perform the changeover operation of the modes and to improve the ease of use of the rotary impact tool.
  • At least one of the speed changer units may be kept in the non-reduction state in the impact mode, the speed changer unit may be kept in the non-reduction being a final planetary reduction unit arranged near the output shaft in the multi-stage speed reduction mechanism, the final planetary reduction unit may be including a sun gear connected to the connector member of the changeover unit through an intermediate transfer member.
  • the final planetary reduction unit is brought into the non-reduction state by releasing the engagement between the sun gear and the planetary gear when the drill driver mode is converted to the impact mode.
  • the final planetary reduction unit may be kept in the non-reduction state in the impact mode includes the IV-type planetary gear unit, the small-diameter gear portion being arranged on the output side of the IV-type planetary gear unit.
  • the IV-type planetary gear unit whose speed reduction can be made greater without increasing the outer diameter thereof is brought into the non-reduction state in the impact mode.
  • This makes it possible to set the high speed mode as the impact mode while setting the low speed mode and the middle speed mode as the drill driver mode.
  • it is possible to set the reduction ratio of the drill driver mode closer to that of the conventional drill-driver-single-function rotary tool.
  • the speed ratio of the drill driver mode to the impact mode can be set into a speed ratio that permits easier use of the rotary impact tool. Since the small-diameter gear portion is arranged on the output side, so is the ring gear of the final planetary reduction unit. Thanks to this feature, it is possible to easily assemble the final planetary reduction unit even when the clutch mechanism is assembled first.
  • the ratio between the teeth number of the small-diameter gear portion and the teeth number of the large-diameter gear portion of the stepped planetary gear may be set equal to 1: natural number.
  • the teeth numbers of the large-diameter gear portion and the small-diameter gear portion can be grasped with ease. This eliminates the need to adjust the positions of teeth when the small-diameter gear portion is coupled to the ring gear. Accordingly, it is possible to easily carry out the assembling work.
  • the changeover unit may include engagement portions respectively provided in the anvil and the hammer and a connector member arranged to engage with the engagement portions, and wherein the drill driver mode and the impact mode are changed over by changing over a state in which the connector member engages with the engagement portions to keep the impact mechanism against relative rotation and a state in which the connector member does not engage with at least one of the engagement portions.
  • the impact mechanism can be held against rotation merely by interconnecting the hammer and the anvil against relative rotation.
  • This makes it possible to simplify the configuration of the changeover unit used in changing over the impact mode and the drill driver mode. Accordingly, it is possible to prevent the increase in the size of the rotary impact tool, which would otherwise occur when the changeover unit becomes complex. It is also possible to easily perform the changeover operation of the modes and to improve the ease of use of the rotary impact tool.
  • the ratio between the number of the stepped planetary gear, the teeth number of the ring gear and the teeth number of the sun gear may be set equal to 1 : natural number : natural number.
  • the small-diameter gear portion and the large-diameter gear portion of the stepped planetary gear may be formed independently of each other so that the relative angle between the small-diameter gear portion and the large-diameter gear portion becomes adjustable.
  • the large-diameter gear portion is formed independently of the small-diameter gear portion. Therefore, the reduction ratio of the IV-type planetary gear unit can be changed merely by changing the teeth number and module of the sun gear and the large-diameter gear portion. Inasmuch as the relative angle between the small-diameter gear portion and the large-diameter gear portion is adjustable, it is possible to easily provide a planetary gear differing in relative angle from other planetary gears. This makes it possible to easily assemble the IV-type planetary gear unit.
  • the three speed modes of the multi-stage speed reduction mechanism may be changed over in the order of the middle speed mode, the low speed mode and the high speed mode.
  • the modes are changed over in the order of the middle speed mode, the low speed mode and the high speed mode.
  • the impact mode and the drill driver low mode used in drilling large-diameter holes are always changed over one next the other.
  • This provides an easy-to-use rotary impact tool capable of performing the changeover operation in the order of the magnitude of torque outputted from the main body.
  • a multi-purpose rotary impact tool of the present invention is operable in an impact mode in which an impact mechanism 6 including a hammer 61 and an anvil 91 is used and in a drill driver mode in which an output shaft 9 is rotated without causing any impact operation to the impact mechanism 6.
  • the impact mode and the drill driver mode can be changed over by a changeover unit which in turn is externally operated through the use of a shift operation unit 14.
  • the multi-purpose rotary impact tool in accordance with a first embodiment of the present invention is of a portable type driven by a built-in power source (not shown).
  • the output power of a motor 13 is transferred to a drive shaft 8 through a multi-stage speed reduction mechanism.
  • An impact output power is applied from the drive shaft 8 to the output shaft 9 through an impact mechanism 6.
  • the side on which the motor 13 lies along the axis of the drive shaft 8 will be referred to as "rear” and the side on which the output shaft 9 lies will be called "front”.
  • the built-in power source is accommodated within a grip portion 11 extending from a housing 1 which forms a shell of the rotary impact tool.
  • a trigger handle 12, a switch for operating the motor 13, is arranged near the root area of the grip portion 11.
  • the impact mechanism 6 includes the drive shaft 8, a hammer 61, an anvil 91, a biasing spring 63 for biasing the hammer 61 toward the anvil 91 and a spring rest 64 for supporting the rear end of the biasing spring 63.
  • steel balls 65 are allowed to engage with a groove-shaped cam defined on the outer circumferential surface of the drive shaft 8 and a groove-shaped cam defined on the inner circumferential surface of the hammer 61.
  • the hammer 61 can rotate together with rotation of the drive shaft 8.
  • the protrusion 62 extending forwards from the hammer 61 comes into engagement with the anvil 91, thereby rotating the anvil 91 and the output shaft 9.
  • the hammer 61 rotates with respect to the drive shaft 8 and moves backwards against the biasing spring 63 along the lead lines of the cams.
  • the protrusion 62 rides over the anvil 91, the hammer 61 is moved forwards along the lead lines of the cams by the biasing force of the biasing spring 63. As a result, the protrusion 62 applies a rotational striking impact to the anvil 91.
  • a multi-stage speed reduction mechanism is arranged between the drive shaft 8 and the motor 13.
  • the speed reduction mechanism includes a plurality of planetary reduction units having different speed reduction ratios.
  • the rotational movement transferred to the output shaft 9 can be changed at a plurality of speed values by combining the reduction state and non-reduction state of the planetary reduction units.
  • the rotary impact tool of the present embodiment includes first, second and third planetary reduction units 2, 3 and 5.
  • the first planetary reduction unit 2 works as a speed reducer unit at all times but the second and third planetary reduction units 3 and 5 serve as speed changer units that can change over a reduction state and a non-reduction state.
  • the first planetary reduction unit 2 includes a first sun gear 21 fixed to an input shaft 132 rotated by the motor 13, a first ring gear 23 fixed to a motor base 131 through which the motor 13 is supported on the housing 1, and a plurality of first planetary gears 22 engaging with both the first sun gear 21 and the first ring gear 23. Since the first ring gear 23 is fixed to the motor base 131, the first planetary reduction unit 2 serves always to reduce the speed of the rotational movement transferred from the motor 13.
  • First transfer shafts 24 are fixedly secured to the respective first planetary gears 22.
  • the rotational movement of reduced speed is transferred to a first carrier 25 through the first transfer shafts 24.
  • a second sun gear 31 of the second planetary reduction unit 3 is provided at the side of the first carrier 25 near the drive shaft 8.
  • the second planetary reduction unit 3 is a speed changer unit that includes the second sun gear 31 arranged in a concentric relationship with the first sun gear 21 of the first planetary reduction unit 2, an axially-slidable second ring gear 33, and a plurality of second planetary gears 32 engaging with both the second sun gear 31 and the second ring gear 33.
  • Second transfer shafts 34 through which to transfer torque to a second carrier 35 are fixed to the respective second planetary gears 32.
  • the second carrier 35 is rotatably supported on the input shaft 132 through a bearing 15.
  • the second ring gear 33 can be axially slid between two positions, namely a rear position adjacent to the motor 13 and a front position near the drive shaft 8.
  • the position of the second ring gear 33 is changed by operating a second shift handle 141 of the shift operation unit 14 provided in the housing 1, and axially sliding the second ring gear 33 through a second shift spring (not shown).
  • the second ring gear 33 engages with the external gear 351 of the second carrier 35 against relative rotation. Accordingly, the second planetary reduction unit 3 rotates as a unit in a non-reduction state in which the second planetary reduction unit 3 does not perform any speed reduction function.
  • the second ring gear 33 If the second ring gear 33 is brought into the rear position by moving the second shift handle 141 backwards as shown in Fig. 2 , the second ring gear 33 disengages from the external gear 351 of the second carrier 35. At this time, the engagement portion 331 axially extending from the second ring gear 33 engages with the engagement portion 231 of the first ring gear 23 against relative rotation.
  • the second planetary reduction unit 3 comes into a reduction state in which the second planetary reduction unit 3 performs a speed reduction function. If the second shift handle 141 is moved forwards, the engagement portions 231 and 331 are disengaged from each other. Thus, the second planetary reduction unit 3 returns to the non-reduction state shown in Fig. 1 .
  • the second planetary reduction unit 3 is a speed changer unit capable of changing over the non-reduction state and the reduction state and consequently changing the speed of the rotational movement transferred from the motor 13.
  • Retainer pins 16 are provided on the front side of the second ring gear 33 to decide the position of the second ring gear 33, when the second ring gear 33 is moved into the front position, and to prevent the second ring gear 33 from being removed forwards.
  • the second carrier 35 includes a plurality of power transfer pins 41 axially protruding forwards, i.e., toward the drive shaft 8.
  • a power transfer carrier 42 is coupled with the power transfer pins 41 so that it can make sliding movement forwards and backwards along the axes of the power transfer pins 41.
  • the power transfer carrier 42 is axially slidable between a rear position nearer to the motor 13 and a front position nearer to the drive shaft 8.
  • the torque of the second carrier 35 is transferred to the power transfer carrier 42 through the power transfer pins 41 regardless of the position of the power transfer carrier 42.
  • the sliding movement of the power transfer carrier 42 is caused through a third shift spring (not shown) by operating a third shift handle 142 of the shift operation unit 14 provided in the housing 1.
  • the third shift handle 142 and the second shift handle 141 are designed to restrain each other's movement. This prevents simultaneous operation of the shift handles 141 and 142 and concurrent occurrence of speed changes in the speed changer units. That is to say, the shift operation unit 14 is configured to perform the speed changing operation step by step.
  • the movement of the third shift handle 142 is restrained by the second shift handle 141 in the state shown in Fig. 1 .
  • the second shift handle 141 is allowed to operate.
  • the second shift handle 141 and the third shift handle 142 are all operable in the state shown in Fig. 2 , which is the middle state between the two states shown in Figs. 1 and 3 . If one of the second shift handle 141 and the third shift handle 142 is operated, the state shown in Fig. 1 or 3 becomes available. Thus, only one of the second shift handle 141 and the third shift handle 142 can be operated.
  • the third planetary reduction unit 5 includes a third sun gear 51 fixedly secured to the front side of the power transfer carrier 42.
  • the third planetary reduction unit 5 further includes a plurality of third planetary gears 52.
  • the third sun gear 51 engages with the third planetary gears 52 when the power transfer carrier 42 is in the front position. If the power transfer carrier 42 moves into the rear position, the third sun gear 51 is disengaged from the third planetary gears 52. This means that the third planetary reduction unit 5 is a speed changer unit shifted in response to the movement of the power transfer carrier 42.
  • the third planetary reduction unit 5 further includes a third ring gear 53.
  • Each of the third planetary gears 52 is a stepped planetary gear that includes a large-diameter gear portion 521 engaging with the third sun gear 51 and a small-diameter gear portion 522 engaging with the third ring gear 53, the small-diameter gear portion 522 being smaller in diameter than the large-diameter gear portion 521.
  • the third planetary reduction unit 5 is a so-called IV-type planetary gear unit belonging to a 2K-H type planetary reduction mechanism.
  • each of the third planetary gears 52 is a two-stage external gear in which the large-diameter gear portion 521 and the small-diameter gear portion 522 are concentrically coupled together against relative rotation.
  • Third transfer shafts 54 for transferring power to a third carrier 55 are fixedly secured to the axes of rotation of the third planetary gears 52, respectively.
  • a clutch mechanism 7 is arranged on the output side of the third planetary reduction unit 5.
  • the clutch mechanism 7 is of a conventional type including a plurality of clutch ridges 71 provided on the front side of the third ring gear 53, a plurality of steel balls 72 positioned between the clutch ridges 71, a thrust plate 73 remaining in contact with the steel balls 72, a clutch spring 74 for biasing the steel balls 72 through the thrust plate 73 and a clutch adjusting thread member 75.
  • the clutch mechanism 7 has the same function as that of the conventional one. If the torque applied to the third ring gear 53 exceeds a predetermined value, the clutch ridges 71 push the steel balls 72 forwards to bring the third ring gear 53 into an idle state. The third carrier 55 stops its rotation as the third ring gear 53 runs idle. This prevents the rotary impact tool from suffering from damage, which would otherwise occur when an excessively high load acts in the drill driver mode. If the clutch mechanism 7 works in the impact mode, there is a possibility that the impact mechanism 6 cannot normally perform its striking operation.
  • Retainer pins 16 are provided on the rear side of the third ring gear 53 to prevent the third ring gear 53 from being pushed backwards by the steel balls 72 of the clutch mechanism 7.
  • a cylindrical intermediate output shaft 56 is fixedly secured to the front side of the third carrier 55 of the third planetary reduction unit 5 so that the torque of the third carrier 55 can be transferred to the intermediate output shaft 56.
  • the rear end of the drive shaft 8 engages with the front end of the intermediate output shaft 56 against relative rotation so that the torque of the intermediate output shaft 56 can be transferred to the drive shaft 8.
  • the third carrier 55 and the intermediate output shaft 56 may be formed into a single unit.
  • the rear end portion of a connector sleeve 43 is fixed to the inner circumference of the power transfer carrier 42.
  • the connector sleeve 43 and the third sun gear 51 are rotated as a unit.
  • the front end portion of the connector sleeve 43 is rotatably inserted through the inner circumference of the intermediate output shaft 56.
  • the connector sleeve 43 is slid together with the third sun gear 51.
  • the connector sleeve 43 includes an intermediate shaft direct-coupling portion 431 formed on the outer circumferential surface of the front end portion thereof.
  • the intermediate output shaft 56 includes a direct-coupling engagement portion 561 provided in the rear section of the inner circumference thereof.
  • the intermediate shaft direct-coupling portion 431 of the connector sleeve 43 engages with the direct-coupling engagement portion 561 of the intermediate output shaft 56 against relative rotation.
  • the engagement between the intermediate shaft direct-coupling portion 431 and the direct-coupling engagement portion 561 is permitted only when the power transfer carrier 42 is moved from the front position to the rear position to have the third sun gear 51 disengaged from the third planetary gears 52.
  • the torque of the power transfer carrier 42 is directly transferred to the intermediate output shaft 56 without passing through the third planetary reduction unit 5.
  • the third planetary reduction unit 5 is kept in a non-reduction state and a non-use state in which no torque is transferred, thereby deactivating the clutch mechanism 7.
  • the third shift handle 142 is operated to move the power transfer carrier 42 from the rear position to the front position, the intermediate shaft direct-coupling portion 431 and the direct-coupling engagement portion 561 are disengaged from each other. At this time, the third sun gear 51 comes into engagement with the third planetary gears 52. Accordingly, the third planetary reduction unit 5 is turned to a reduction state, consequently activating the clutch mechanism 7.
  • Retainer plates 17 that keep the second carrier 35, the second ring gear 33 and the third planetary gears 52 from falling into the movement space in which the power transfer carrier 42 makes sliding movement are provided at the axial opposite ends of the movement space of the power transfer carrier 42.
  • the position of the retainer plates 17 is decided by the retainer pins 16 arranged on the front side of the second ring gear 33. It goes without saying that the third sun gear 51 and the connector sleeve 43 may be integrally formed with the power transfer carrier 42.
  • the drive shaft 8 to which torque is transferred from the intermediate output shaft 56 has an axially extending bore defined on the inner circumference thereof.
  • a changeover pin 45 is rotatably and axially slidably arranged inside the bore of the drive shaft 8 in a concentric relationship with the drive shaft 8.
  • the changeover pin 45 is provided at its front end with a connector piece 44 that serves as a changeover unit for changing over the impact mode and the drill driver mode.
  • the connector piece 44 is rotatable but axially immovable with respect to the changeover pin 45.
  • the drive shaft 8 includes a drive shaft side engagement portion 81 provided in the bore thereof.
  • the anvil 91 includes an anvil side engagement portion 92.
  • the connector piece 44 can engage with the drive shaft side engagement portion 81 and the anvil side engagement portion 92 in an axially slidable manner against relative rotation.
  • engagement portions 81 and 92 provided in the drive shaft 8 and the anvil 91 are relatively rotatable without interfering with each other, they can be interconnected by the connector piece 44 against relative rotation.
  • the connector piece 44 engages with both the drive shaft side engagement portion 81 and the anvil side engagement portion 92, the engagement portions 81 and 92 are kept against relative rotation by the connector piece 44. Thus, the drive shaft 8 and the anvil 91 are connected to each other. If one of the engagement portions 81 and 92 is disengaged from the connector piece 44, the drive shaft 8 and the anvil 91 come into a relatively rotatable state again.
  • the rear end of the changeover pin 45 is press-fitted into the front end of the connector sleeve 43 to rotate together with the power transfer carrier 42.
  • the changeover pin 45 and the connector sleeve 43 are slid forwards and backwards along with the sliding movement of the power transfer carrier 42.
  • the connector piece 44 comes into either a state in which the connector piece 44 engages with only the drive shaft side engagement portion 81 and not the anvil side engagement portion 92 or a state in which the connector piece 44 engages with both the drive shaft side engagement portion 81 and the anvil side engagement portion 92.
  • the engagement portions 81 and 92 can make relative rotation and the torque of the drive shaft 8 is transferred to the anvil 91 and the output shaft 9 through the impact mechanism 6. This establishes an impact mode in which a task is performed with an intermittently-applied rotational impact force.
  • the connector piece 44 is rotatable with respect to the changeover pin 45 which in turn remains rotatable with respect to the drive shaft 8. Therefore, even when the rotational speed of the changeover pin 45 becomes different than that of the connector piece 44 or the drive shaft 8, there is no possibility that the changeover pin 45 is twisted and severed or the connector piece 44 and the engagement portions 81 and 92 are damaged.
  • the connector piece 44 may engage with only the anvil side engagement portion 92 and not the drive shaft side engagement portion 81.
  • the shape of the connector piece 44 may be suitably changed insofar as such change does not hinder the operation of the impact mechanism 6 in the impact mode nor cause the impact operation to be performed in the drill driver mode.
  • the impact mode refers to the state in which the second shift handle 141 and the third shift handle 142 are all positioned at the rear side.
  • the second ring gear 33 and the power transfer carrier 42 lie in the rear position. This establishes a high speed mode in which the second planetary reduction unit 3 is in the reduction state and the third planetary reduction unit 5 is in the non-reduction state.
  • the changeover pin 45 Since the power transfer carrier 42 is in the rear position, the changeover pin 45 is moved backwards. As a result of the backward movement of the changeover pin 45, the connector piece 44 is disengaged from the anvil side engagement portion 92 so that the impact mechanism 6 can work.
  • the third sun gear 51 is kept out of engagement with the third planetary gears 52, as a result of which no torque is applied to the third ring gear 53.
  • the clutch mechanism 7 does not work during the impact mode. This eliminates the need to perform an additional operation which would otherwise be needed to deactivate the clutch mechanism 7.
  • the power transfer carrier 42 is moved to the front position.
  • the third sun gear 51 comes into engagement with the large-diameter gear portions 521 of the third planetary gears 52, thereby bringing the third planetary reduction unit 5 into a reduction state.
  • the forward movement of the power transfer carrier 42 results in forward movement of the changeover pin 45. Therefore, the connector piece 44 engages with the anvil side engagement portion 92 as well as the drive shaft side engagement portion 81, thereby interconnecting the drive shaft 8 and the anvil 91 against relative rotation. Accordingly, the impact mode is converted to a drill driver mode.
  • the planetary reduction units 2, 3 and 5 are all in the reduction state. This establishes the low speed mode of the three speed modes. In other words, there is established a drill driver low mode in which large-diameter holes can be drilled as in the low speed mode of the conventional drill-driver-single-function rotary tool. Needless to say, the clutch mechanism 7 serves as a torque clutch because the third planetary reduction unit 5 is operated as a reduction unit.
  • the drill driver high mode becomes the middle speed mode of the three speed modes and the impact mode becomes the high speed mode.
  • the reduction ratio of the first planetary reduction unit 2 is set equal to, e.g., about 1/3.3, the reduction ratio of the second planetary reduction unit 3 being equal to, e.g., about 1/3 and the reduction ratio of the third planetary reduction unit 5 being equal to, e.g., about 1/6.
  • the reduction ratio in the drill driver high mode is about 1/20, the reduction ratio in the impact mode being about 1/10.
  • the speed ratio between the high speed mode and the middle speed mode is approximately 1:2 which is the same as the ratio between the reduction ratios of the speed changer units kept in the reduction state during the high speed mode and the middle speed mode.
  • the reduction ratio in the drill driver low mode i.e., in the low speed mode, is about 1/60 and the ratio between the reduction ratios of the high speed mode and the low speed mode is approximately 6:1. If the reduction ratio of the second planetary reduction unit 3 is smaller than that of the third planetary reduction unit 5, the drill driver high mode becomes the high speed mode and the impact mode becomes the middle speed mode.
  • each of the third planetary gears 52 includes a small-diameter gear member 58 formed of a spur gear and a large-diameter gear member 57 made of a spur gear, both of which are coupled together.
  • the teeth number of the large-diameter gear member 57 is equal to the natural-number multiple of the teeth number of the small-diameter gear member 58.
  • the large-diameter gear member 57 has an outer diameter greater than that of the small-diameter gear member 58 (or 522).
  • a polygonal engagement protrusion 581 extends axially from one axial end surface, i.e., one planar surface, of the small-diameter gear member 58.
  • An axially-opened polygonal engagement hole 571 for receiving the engagement protrusion 581 is formed in the planar surface of the large-diameter gear member 57.
  • the small-diameter gear member 58 and the large-diameter gear member 57 are fixed to each other against relative movement in a concentric relationship with the axis of rotation.
  • the planar surface of the small-diameter gear member 58 faces toward and makes contact with the corresponding planar surface of the large-diameter gear member 57.
  • the engagement protrusion 581 and the engagement hole 571 have the shape of an equilateral polygon, the respective sides of which are substantially equal to one another. This makes it possible to couple the small-diameter gear member 58 (or 522) to the large-diameter gear member 57 (or 521) together in a state in which the tip ends of the teeth of the gear members 56 and 57 are aligned with each other as illustrated in Fig. 5A .
  • the relative angle between the small-diameter gear member 58 (or 522) and the large-diameter gear member 57 (or 521) may be changed so that the tip ends of the teeth of the small-diameter gear member 58 can be aligned with the inter-teeth valleys of the large-diameter gear member 57 as illustrated in Fig. 6 .
  • the tip ends of the teeth of the small-diameter gear member 58 may be alternately aligned with the tip ends and inter-teeth valleys of the large-diameter gear member 57 in a specified period.
  • the relative angle between the gear members 56 and 57 can be easily changed in conformity with the desired reduction ratio.
  • the loss of transferred torque is suppressed by forming each of the stepped planetary gears with separable members.
  • the engagement protrusion 581 of substantially regular octagon shape is provided at its center with a bore into which each of the third transfer shafts 54 are inserted.
  • the engagement protrusion 581 may be replaced by a plurality of protrusions formed on the outer circumference of the bore at an equal interval about the axis of rotation.
  • the engagement protrusion 581 may be provided in the large-diameter gear member 57 insofar as it is possible to prevent the increase in size and minimize the loss of transferred torque while obtaining the strength required for the stepped planetary gears to serve as a speed reduction mechanism.
  • the shape of the engagement protrusion 581 and the engagement hole 571 can be suitably changed depending on the design considerations.
  • the outer diameter of the multi-stage speed reduction mechanism can be made smaller than that of the conventional mechanism in which a reduction ratio of about 1/10 is achieved by single-stage reduction. This helps minimize the increase in size.
  • the strength required in the present planetary reduction mechanism is not greater than that required in the conventional reduction mechanism in which the desired reduction ratio in the impact mode is obtained through single stage reduction. Accordingly, it is possible to suppress an increase in the outer diameter and total length of the multi-stage speed reduction mechanism. Even when the performance in the impact mode is improved, it is possible to minimize the increase in the overall size of the rotary impact tool.
  • the multi-stage speed reduction mechanism is capable of establishing three different speeds, one for the impact mode and the remaining two for the drill driver mode. This makes it possible to set the drill driver mode with a reduction ratio closer to that of the conventional drill-driver-single-function rotary tool.
  • the ratio between the reduction ratios of the impact mode and the drill driver mode is about 3:1.
  • the ratio between the reduction ratios of the impact mode and the drill driver high mode is approximately 2:1 and the ratio between the reduction ratios of the impact mode and the drill driver low mode is approximately 6:1if the high speed mode is used as the impact mode. This enables the present rotary impact tool to operate in the drill driver mode with the output torque closer to that of the special-purpose tool for drill driver use having a high speed mode and a low speed mode.
  • the speed changer unit brought into the reduction state in the high speed mode differs from the speed changer unit that comes into the reduction state in the middle speed mode. This ensures that the speed ratio between the high speed mode and the middle speed mode becomes the same as the ratio between the reduction ratios of the speed changer units kept in the reduction state during the high speed mode and the middle speed mode.
  • the operating condition in the drill driver mode can be set closer to the operating condition of the special-purpose tool having only a drill driver function. This enhances the ease of use of the present rotary impact tool.
  • the ratio between the reduction ratios of the impact mode and the drill driver high mode is set equal to about 2:1.
  • the ratio between the speed ratios of the impact mode and the drill driver mode is no more than 3:1. This has been one of the causes that reduce the performance in the drill driver mode in which screws are tightened at a low speed.
  • the middle speed changer unit of the two high speed and middle speed changer units which stays in the reduction state during the middle speed mode, is formed of a IV-type planetary gear unit.
  • the speed reduction of the middle speed changer unit can be made greater than the speed reduction of the conventional planetary reduction mechanism in which a sun gear and a ring gear have the same pitch circle diameter. Therefore, the middle speed changer unit whose speed reduction needs to be greater than that of the high speed changer unit staying in the reduction state during the high speed mode can be designed to have substantially the same outer diameter as that of the high speed changer unit. This makes it possible to minimize the increase in overall size.
  • the reduction ratio of the IV-type planetary gear unit is assumed to be about 1/6
  • the reduction ratio of the conventional planetary reduction mechanism in which a sun gear and a ring gear have the same pitch circle diameter is nothing more than 1/4.
  • the conventional planetary reduction mechanism is designed to have the same reduction ratio as that of the IV-type planetary gear unit, a problem occurs in the strength of the respective gears.
  • the IV-type planetary gear unit is employed in the final or third planetary reduction unit 5. Therefore, the third planetary gears 52 and the third sun gear 51 can be assembled with ease even when the third ring gear 53 having the clutch ridges 71 of the clutch mechanism 7 is assembled first. This is because the third planetary gears 52 are of the stepped type and because the small-diameter gear portions 522 of the third planetary gears 52 engage with the third ring gear 53.
  • Use of the IV-type planetary gear unit makes it easy to perform maintenance and repair, thereby making the rotary impact tool easily usable for a prolonged period of time.
  • the modes are changed over by the shift handles in the order of the high speed mode, the low speed mode and the middle speed mode. This means that the changeover operation between the neighboring modes is performed by shifting only one speed changer unit, which helps prevent the shift mechanism from becoming complicated. Accordingly, it is possible to suppress the increase in the size of the shift mechanism and to minimize the increase in the overall size of the rotary impact tool.
  • the shift operation can be performed only by operating one of the two shift handles. This eliminates the possibility that two or more speed changer units are simultaneously shifted, thereby reducing the likelihood of occurrence of trouble or other problems and making the rotary impact tool easily usable for a prolonged period of time.
  • the low speed mode is positioned between the middle speed mode and the high speed mode. Therefore, the modes are changed over in the order of the impact mode, the drill driver low mode and the drill driver high mode.
  • This provides an easy-to-use rotary impact tool capable of performing the changeover operation in the order of the magnitude of torque outputted from the main body.
  • the two shift handles may be operated at one time to directly convert the impact mode to the drill driver high mode.
  • the third sun gear 51 of the final planetary reduction unit kept in the non-reduction state is disengaged from the third planetary gears 52. This makes it possible to bring the final planetary reduction unit into a non-use state in which no torque is applied thereto. Therefore, there is no need to provide an additional unit for deactivating the clutch mechanism 7. This helps suppress the increase in the overall size and make the rotary impact tool simple in structure.
  • the conversion between the operation and non-operation of the impact mechanism 6, which is important in changing over the impact mode and the drill driver mode, is performed by engaging and disengaging the connector piece 44 and the anvil 91.
  • These engagement and disengagement operations of the connector piece 44 and the anvil 91 are linked to the shift operations of the speed changer units performed when changing over the impact mode and the drill driver mode.
  • the linkage mechanism consists of only the changeover pin 45 rotatably fitted to the drive shaft 8. This makes it possible to realize the linkage mechanism with a simple structure, thereby suppressing the increase in the overall size of the rotary impact tool.
  • the ratio between the teeth number of the small-diameter gear portion 522 and the teeth number of the large-diameter gear portion 521 of each of the third planetary gears 52 is set equal to 1 : natural number. This eliminates the need to adjust the positions of teeth when the small-diameter gear portion 522 is coupled to the third ring gear 53. Accordingly, it is possible to easily carry out the assembling work of the third planetary reduction unit 5.
  • the ratio between the number of the stepped planetary gears, the teeth number of the ring gear meshing with the stepped planetary gears and the teeth number of the sun gear meshing with the stepped planetary gears is set equal to 1 : natural number : natural number.
  • Each of the third planetary gears 52 is formed of the small-diameter gear portion 522 and the large-diameter gear portion 521, both of which are coupled together so that the relative angle therebetween can be changed. Therefore, the reduction ratio can be changed by changing the teeth number and module of the third sun gear 51 and the teeth number and module of the large-diameter gear member 57.
  • the task of changing the reduction ratio can be easily performed without having to replace the third ring gear 53 in which the clutch mechanism 7 is arranged. Furthermore, it becomes possible to easily change the middle speed mode to produce desired output torque.
  • the relative angle between the small-diameter gear portion 522 and the large-diameter gear portion 521 is adjustable, it is possible to easily provide a stepped planetary gear differing in relative angle from the remaining stepped planetary gears if such a need exists. It is also possible to easily assemble the third planetary reduction unit 5, i.e., the IV-type planetary gear unit.
  • the rotational axes of the multi-stage speed reduction mechanism, the clutch mechanism 7, the drive shaft 8 and the output shaft 9 are all arranged in a concentric relationship with the motor 13. This assists in suppressing the increase in the overall size of the rotary impact tool.
  • FIG. 7A and 7B there is shown a rotary impact tool in accordance with a second embodiment of the present invention.
  • engagement portions 611 and 93 are provided on the outer circumferences of the hammer 61 and the anvil 91 and a connector member is provided which can engage with the engagement portions 611 and 93.
  • the present embodiment is directed to claim 9. Only the differing points of the second embodiment from the first embodiment will be described with the common configurations omitted from description.
  • the connector member is a hammer ring 46 slidably engaging with the outer circumference of the hammer 61 and engaging with the engagement portion 611 of the hammer 61 against relative rotation at all times as shown in Fig. 8 .
  • An interlock operation portion 47 is provided so that it can slide forwards and backwards in an axial direction. Upon operating the interlinking operation portion 47 from the outside, the hammer ring 46 is slid forwards or backwards together with the interlock operation portion 47.
  • the hammer ring 46 is provided with a ring groove 462 on its outer circumference.
  • the interlock operation portion 47 is provided with an engagement piece 471 whose width is substantially equal to the axial width of the ring groove 462.
  • the engagement piece 471 is arranged inside the ring groove 462. If the interlock operation portion 47 is slidingly moved forwards or backwards, the hammer ring 46 makes sliding movement in the forward or backward direction.
  • the ring groove 462 has an annular shape, the engagement between the engagement piece 471 and the ring groove 462 is not released even when the hammer ring 46 engaging with the engagement piece 471 rotates together with the hammer 61. At this time, the interlock operation portion 47 does not make rotation.
  • the hammer ring 46 is provided at its front end with a hammer ring claw 461 releasably engageable with the engagement portion 93 of the anvil 9.
  • the hammer ring claw 461 is provided flush with the surface of the protrusion 62 of the hammer 61 that makes contact with the anvil 91.
  • the hammer ring claw 461 comes into engagement with the engagement portion 93 of the anvil 91 against relative rotation. At this time, the hammer ring claw 461 rotates together with the anvil 91 at all times, which prevents the hammer 61 from making backward movement. This establishes the drill driver mode in which the impact mechanism 6 is kept inoperable.
  • the hammer ring 46 is caused to slide backwards by operating the interlock operation portion 47, the hammer ring claw 461 is disengaged from the engagement portion 93 of the anvil 91. As a result, only the protrusion 62 of the hammer 61 and the anvil 91 engage with each other. This establishes the impact mode in which the impact mechanism 6 can work.
  • a clutch fixing ring 48 that does not rotate with respect to the housing 1 but can slide together with the interlock operation portion 47 is arranged at the rear end of the interlock operation portion 47.
  • the clutch fixing ring 48 is releasably engageable with the engagement portion provided on the outer circumference of the third ring gear 53 of the third planetary reduction unit 5 which includes the clutch mechanism 7.
  • the clutch mechanism 7 is activated or deactivated by bringing the clutch fixing ring 48 into engagement or out of engagement with the engagement portion.
  • the clutch fixing ring 48 includes a plurality of claws 481 arranged on its inner circumference at a regular interval.
  • the claws 481 are engageable and disengageable with the engagement portion of the third ring gear 53.
  • the engagement portion of the third ring gear 53 includes an annular recess portion 531 opened radially outwards.
  • the third ring gear 53 includes an outer gear 532 arranged at the rear side of the recess portion 531.
  • a rotary impact tool in accordance with a third embodiment of the present invention.
  • the changeover between the impact mode and the drill driver mode performed by the connector piece 44 in the first embodiment is combined with the changeover of the clutch mechanism 7 performed by the clutch fixing ring 48 in the second embodiment. Only the differing points of the third embodiment from the first and second embodiments will be described with the common configurations omitted from description.
  • a mode converter member 49 slidable along the power transfer pins 41 is additionally installed in the space in which the power transfer carrier 42 can make sliding movement with respect to the power transfer pins 41.
  • the changeover pin 45 is press-fitted to the mode converter member 49. This means that the changeover pin 45 is rotatable with respect to the power transfer carrier 42 and the connector sleeve 43.
  • the mode converter member 49 and the clutch fixing ring 48 can be slid forwards and backwards by a mode-converting operation unit (not shown). If the clutch fixing ring 48 slides backwards, so does the mode converter member 49.
  • the clutch mechanism 7 is deactivated by the movement of the clutch fixing ring 48. Furthermore, the changeover pin 45 slides backwards and the connector piece 44 engages with only the drive shaft side engagement portion 81, thereby establishing the impact mode.
  • the mode-converting operation unit is operated from the outside in the impact mode so that the clutch fixing ring 48 can slide forwards to activate the clutch mechanism 7, the mode converter member 49 is also slid forwards. At this time, the connector piece 44 engages with the anvil side engagement portion 92, whereby the impact mode is converted to the drill driver mode.
  • the power transfer carrier 42 is slidable forwards and backwards without interfering with the mode converter member 49. This makes it possible to change over the third planetary reduction unit 5 between a shifting state and a non-shifting state.
  • the speed-changing operation performed by the shift operation unit 14 is independent of the changeover operation between the impact mode and the drill driver mode performed by the mode-converting operation unit. This makes it possible to realize three speeds in each of the impact mode and the drill driver mode, thereby improving the ease of use of the rotary impact tool.
  • the number of the speed changer units is not limited to two but may be three or more so that two or more speeds can be available in the impact mode and three or more speeds in the drill driver mode.
  • the design of the multi-stage speed reduction mechanism may be appropriately changed, insofar as it is always possible to reduce the speed in two or more stages and to change the speed in three or more speed ratios through the use of at least one speed reducer unit and at least one speed changer unit in the respective modes and insofar as it is possible to obtain the advantageous effects of the present invention.
  • the operation units such as the shift operation unit 14 and the mode-converting operation unit are not limited to the axially slidable type but may be of a circumferentially rotatable type in which the rotational movement is translated into axial sliding movement through a cam.
  • the design of the operation units may be suitably changed insofar as it is possible to obtain the advantageous effects of the present invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Drilling And Boring (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Retarders (AREA)
  • Percussive Tools And Related Accessories (AREA)

Claims (12)

  1. Outil rotatif à percussion comprenant :
    une source de puissance d'entraînement (13) destinée à produire une puissance de rotation ;
    un arbre de sortie (9) destiné à recevoir la puissance de rotation ;
    un mécanisme de percussion (6) comprenant un marteau (61) et une enclume (91) ;
    une unité de commutation destinée à commuter entre un mode percussion dans lequel le mécanisme de percussion (6) est actionné, et un mode entraînement de foret dans lequel la puissance de rotation produite par la source de puissance d'entraînement (13) est transférée à l'arbre de sortie (9) sans actionner le mécanisme de percussion (6) ; et
    un mécanisme de réduction de vitesse à plusieurs étages (2, 3, 5) destiné à transférer la puissance de rotation produite par la source de puissance d'entraînement (13) à l'arbre de sortie (9) à des vitesses variables dans trois modes de vitesse au moins comprenant un mode à vitesse réduite, un mode à vitesse intermédiaire et un mode à vitesse élevée ;
    dans lequel le mécanisme de réduction de vitesse à plusieurs étages (2, 3, 5) comprend au moins deux unités de sélection de vitesse planétaires (3, 5) pouvant être commutées entre un état de réduction et un état de non réduction et au moins une unité de réduction de vitesse (2) fonctionnelle dans un état de réduction à tout moment, l'un au moins des trois modes de vitesse au moins étant utilisé en tant que mode percussion, deux au moins des trois modes de vitesse au moins étant utilisés en tant que mode entraînement de foret, les trois modes de vitesse étant établis par l'intermédiaire d'opérations de réduction de vitesse de deux étages ou plus dans lequel l'unité de réduction de vitesse (2) et l'une au moins des unités de sélection de vitesse (3, 5) sont maintenues dans l'état de réduction.
  2. Outil rotatif à percussion selon la revendication 1, dans lequel l'une des deux unités de sélection de vitesse planétaires (3 ou 5) prend l'état de réduction dans le mode à vitesse intermédiaire et l'autre (3 ou 5) prend l'état de réduction dans le mode à vitesse élevée, le rapport de vitesse entre le mode à vitesse élevée et le mode à vitesse intermédiaire étant fixé égal au rapport entre les rapports de réduction des deux unités de sélection de vitesse planétaires (3, 5).
  3. Outil rotatif à percussion selon la revendication 2, dans lequel l'unité de sélection de vitesse planétaire (5) qui prend l'état de réduction dans le mode à vitesse intermédiaire, comprend une unité d'engrenages planétaires de type IV qui comprend un planétaire (51), une couronne dentée (53) et des engrenages planétaires échelonnés (52), chacun des engrenages planétaires échelonnés (52) comprenant une partie d'engrenage à grand diamètre (57 ou 521) et une partie d'engrenage à petit diamètre (58 ou 522), la partie d'engrenage à grand diamètre (57 ou 521) différant par le nombre de dents et par le diamètre extérieur de la partie d'engrenage à petit diamètre (58 ou 522), la partie d'engrenage à grand diamètre (57 ou 521) venant en prise avec le planétaire (51), la partie d'engrenage à petit diamètre (58 ou 522) venant en prise avec la couronne dentée (53).
  4. Outil rotatif à percussion selon l'une quelconque des revendications 1 à 3, dans lequel l'unité de réduction de vitesse (2) est une première unité de réduction planétaire (2) disposée à proximité de la source de puissance d'entraînement (13) dans le mécanisme de réduction de vitesse à plusieurs étages (2, 3, 5).
  5. Outil rotatif à percussion selon la revendication 1, comprenant en outre un arbre d'entraînement (8) entraîné par la puissance de rotation fournie par la source de puissance d'entraînement (13), dans lequel l'unité de commutation comprend des parties de mise en prise (92, 81) disposées de manière respective dans l'enclume (91) et dans l'arbre d'entraînement (8) venant en prise avec le marteau (61) et un élément de connecteur disposé de façon à venir en prise avec les parties de mise en prise (92, 81), et dans lequel le mode entraînement de foret et le mode percussion sont commutés en commutant entre un état dans lequel l'élément de connecteur vient en prise avec les parties de mise en prise (92, 81) de façon à interconnecter l'enclume (91) et l'arbre d'entraînement (8) vis-à-vis d'une rotation relative, et un état dans lequel l'élément de connecteur ne vient pas en prise avec l'une au moins des parties de mise en prise (92, 81).
  6. Outil rotatif à percussion selon la revendication 5, dans lequel l'une au moins des unités de sélection de vitesse (5) est maintenue dans l'état de non réduction dans le mode percussion, l'unité de sélection de vitesse (5) maintenue dans l'état de non réduction étant une unité de réduction planétaire finale disposée à proximité de l'arbre de sortie (9) dans le mécanisme de réduction de vitesse à plusieurs étages (2, 3, 5), l'unité de réduction planétaire finale comprenant un planétaire (51) connecté à l'élément de connecteur de l'unité de commutation par un élément de transfert intermédiaire.
  7. Outil rotatif à percussion selon la revendication 3, comprenant en outre un arbre d'entraînement (8) entraîné par la puissance de rotation fournie par la source de puissance d'entraînement (13), dans lequel l'unité de commutation comprend des parties de mise en prise (92, 81) disposées de manière respective dans l'enclume (91) et dans l'arbre d'entraînement (8) venant en prise avec le marteau (61) et un élément de connecteur disposé de façon à venir en prise avec les parties de mise en prise (92, 81), et dans lequel le mode entraînement de foret et le mode percussion sont commutés en commutant entre un état dans lequel l'élément de connecteur vient en prise avec les parties de mise en prise (92, 81) de façon à interconnecter l'enclume (91) et l'arbre d'entraînement (8) vis-à-vis d'une rotation relative, et un état dans lequel l'élément de connecteur ne vient pas en prise avec l'une au moins des parties de mise en prise (92, 81) ;
    l'une au moins des unités de sélection de vitesse (5) est maintenue dans l'état de non réduction dans le mode percussion, l'unité de sélection de vitesse (5) maintenue dans l'état de non réduction étant une unité de réduction planétaire finale disposée à proximité de l'arbre de sortie (9) dans le mécanisme de réduction de vitesse à plusieurs étages (2, 3, 5), l'unité de réduction planétaire finale comprenant un planétaire (51) connecté à l'élément de connecteur de l'unité de commutation par un élément de transfert intermédiaire ; et
    l'unité de réduction planétaire finale maintenue dans l'état de non réduction dans le mode percussion comprend l'unité d'engrenages planétaires de type IV, la partie d'engrenage à petit diamètre (58 ou 522) étant disposée du côté de la sortie de l'unité d'engrenages planétaires de type IV.
  8. Outil rotatif à percussion selon la revendication 3 ou la revendication 7, dans lequel le rapport entre le nombre de dents de la partie d'engrenage à petit diamètre (58 ou 522) et le nombre de dents de la partie d'engrenage à grand diamètre (57 ou 521) de chacun des engrenages planétaires échelonnés (52) est fixé égal à 1 / un nombre entier naturel.
  9. Outil rotatif à percussion selon l'une quelconque des revendications 1 à 4, dans lequel l'unité de commutation comprend des parties de mise en prise (93, 611) disposées de manière respective dans l'enclume (91) et dans le marteau (61) et un élément de connecteur agencé de façon à venir en prise avec les parties de mise en prise (93, 611), et dans lequel le mode entraînement de foret et le mode percussion sont commutés en commutant entre un état dans lequel l'élément de connecteur vient en prise avec les parties de mise en prise (93, 611) de façon à maintenir le mécanisme de percussions (6) vis-à-vis d'une rotation relative, et un état dans lequel l'élément de connecteur ne vient pas en prise avec l'une au moins des parties de mise en prise (93, 611).
  10. Outil rotatif à percussion selon l'une quelconque des revendications 3, 7 et 8, dans lequel le rapport entre le nombre d'engrenages planétaires échelonnés (52), le nombre de dents de la couronne dentée (53) et le nombre de dents du planétaire (51), est fixé égal à 1 / un nombre entier naturel / un nombre entier naturel.
  11. Outil rotatif à percussion selon l'une quelconque des revendications 3, 7, 8 et 10, dans lequel la partie d'engrenage à petit diamètre (58 ou 522) et la partie d'engrenage à grand diamètre (57 ou 521) de chacun des engrenages planétaires échelonnés (52) sont formées de manière indépendante l'une de l'autre de telle sorte que l'angle relatif entre la partie d'engrenage à petit diamètre (58 ou 522) et la partie d'engrenage à grand diamètre (57 ou 521) puisse être réglé.
  12. Outil rotatif à percussion selon l'une quelconque de revendications 1 à 11, dans lequel les trois modes de vitesse au moins du mécanisme de réduction de vitesse à plusieurs étages (2, 3, 5) sont commutés dans l'ordre suivant : mode à vitesse intermédiaire, mode à vitesse réduite et mode à vitesse élevée.
EP10000820A 2009-01-27 2010-01-27 Outil d'impact rotatif Active EP2210708B8 (fr)

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JP2009015944A JP4674640B2 (ja) 2009-01-27 2009-01-27 インパクト回転工具

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EP2210708A2 EP2210708A2 (fr) 2010-07-28
EP2210708A3 EP2210708A3 (fr) 2011-04-06
EP2210708B1 true EP2210708B1 (fr) 2012-09-19
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Publication number Publication date
EP2210708A3 (fr) 2011-04-06
JP2010172982A (ja) 2010-08-12
US20100186978A1 (en) 2010-07-29
EP2210708B8 (fr) 2012-12-05
JP4674640B2 (ja) 2011-04-20
EP2210708A2 (fr) 2010-07-28
US8381831B2 (en) 2013-02-26
CN101786266A (zh) 2010-07-28
CN101786266B (zh) 2012-06-27

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